Fluid pressure rotary motor with spring actuated swinging vanes



Nov. 4, 1947. H. J. SHARP 2,430,251

FLUID PRESSURE ROTARY MOTOR WITH SPRING ACTUATED SWINGING VANES FiledSept. 7, 1944 4 Sheets-Sheet -1 Weill Or: HENRY sHARPX V i wwmjj FLUIDPRESSURE ROTARY MOTOR WITH SPRING ACTUATED SWINGING VANES Filed Sept. 7,1944 4 Sheets-She et 2 HENRY Q; SHARP Nov.4, 1947. S ARP 2,430,251

FLUID PRESSURE ROTARY MOTOR WITH SPRING ACTUATED SWINGING VANES FiledSept. 7, 1944 4 sheets-s et a any A $4 Mentor 7 "HENRY msnmzp Nov. 4,1947. SHARP I 2,430,251 I FLUID PRESSURE ROTARY MOTOR WITI-i SPRINGACTUATED SWINGING V ANES Filed Sept. 7.11944 4 Sheets-Sheet 4 HENRY J.@HAR'P Inderdor:

Patented Na. 4, 1947 ITED STATE OFFICE Henry J. Sharp, Upper Darby, Pa.Application September '7, 1944, Serial No. 553,083

3 Claims. 1

The present invention relates to fluid impelled rotary motors or enginesand is more particularly directed to a fluid operated rotary motor whichis so constructed and designed that the friction power losses within theengine are reduced to a minimum with the consequence that temperaturerises are low, the elliciency of the engine is relatively high and as aresult the ratio of weight of the engine to the power delivered by it islow.

The present invention relates particularly to the type of engine whichis operated b compressed fluids and which consists essentially of afixed casing or stator and a rotary element or rotor disposed withinsaid casing. In this type of motor or engine the rotor is eccentric withreference to the stator and is provided on its periphery with a seriesof pivoted vanes or impellers. The outer ends or faces of such vanesmove against the inner cylindrical face of the stator while the vanesreceive the pressure of theoperating fluid and are impelled thereby torotate the rotor.

The vanes generate considerable friction and heat and also causesubstantial wear on the cooperating parts. It is the aim of the presentinvention to minimize these sources of power loss in the engine which inthis type of apparatus known hitherto greatly reduce the efiiciency ofthe engine.

For these purposes, the present invention minimizes the relative motionbetween the operating ends of the impeller vanes and the cooperatingface of the stator without reducing the rotation of the rotor.

A still further object of the present invention is to provide astructure of the type described and in which the relative motion betweenthe impeller vanes and the cooperating face of the stator is at aminimum where the pressure is at a maximum and where the friction losseswould otherwise be at a maximum.

To accomplish these purposes the present invention provides the statorwith an annular rotary element which is rotated by reason of thepressure exerted against its inner face by the impeller vanes of therotor. Preferably, one or more races of ball bearings are interposedbetween this rotary annular element and the fixed annular portion of thestator. As a consequence of this organization the annular rotary elementrotates with the rotor on the ball bearings.

Another object of the present invention is to provide readily operablemeans for adjusting the assembly to compensate for wear of theimpellers, and of the bearing races.

Another object of the present invention is to provide a structure of thetype described which may be manufactured, assembled and repairs madewith great facility.

With the above objects in view, the invention further resides in thecombination and arrange--. ment of parts and in the details ofconstruction herein described and claimed; it being understood that thespecific embodiments of the invention described herein are illustrativeand that modifications thereof falling within the scope of the appendedclaims will become apparent to persons skilled in the art.

In the accompanying drawings:

Figure l is a plan view of the preferred embodiment of the invention.

Fig. 2 is a sectional view on line 22 of Fig. 1.

Fig. 3 is a sectional view on line 3-3 of Fig. 2.

Fig. 4 is a sectional view of one of the plates of the stator.

Fig. 5 is a perspective of one of the impeller vanes.

Fig. 6 is an edge view of the same.

Fig. 7 is a plan view of the same.

Fig. 8 is an enlarged showing of the detail.

Fig. 9 is a perspective view of a part of the fixed cylindrical portionof the stator.

Fig. 10 is a sectional view of the invention as embodied in thetwo-stage engine.

Referring particularly to Figure 2 of the drawings, the referencecharacter 20 indicates the stator of the rotary engine embodying thepresent invention and the reference character 2| indicates the rotor ofthe engine.

The rotor 2i comprises a circular disk 22 provided with a central shaftl9 spliced or keyed to the rotor, the shaft !9 having a drive pulley I!mounted at one end for the delivery of power generated by the motor. Theimpeller vanes are shown in detail in Figures 5, 6 and. 7. As shown inthe present invention eight such vanes 23 are mounted on the peripheryof the rotor disk 22. It will be understood, howeventhat the number ofthe impeller vanes may be varied depending upon the capacity and rate ofrevolution of the engine. Each vane 23 which may be in form of a castingcomprising a bearing sleeve 24 at its heel and an integral suitablyshaped vane portion 25. The portion 25 comprises a fiat face 25 and asuitably curved face 2?. The flat face 26 carries a layer of flexibleand yieldable material such as leather or the like 28, which has aportion 28 extending beyond the operating edge 30 or the toe of thevane. The leather gasket 23 also extends beyond the lateral edges of thevane. A piece of sheet metal 3| is disposed over the gasket .28 and theelements 25, 28 and 3| are held togetherby means of screws or pins 16.The gasket 28 is readily replaceable.

The rotor disk 22 is provided with a plurality of recesses or seats 32designed to receive the vanes 23 when the same are in their collapsedposition as shown at 33 and .34. L'I'hecurvature of the outer face 21 isof the sameradiusas the disk 22 with the result that when the vanes arein their collapsed positions shown "at 33 and, these faces 21 aresubstantially continuous with the portions l8 of the periphery orcylindrical face of the disk 22.

The recess 32 is :provided .at one :end with a transverse depression "toreceive :the cylindrical bearing portion 24 ofthe vane. The .rotor isalso providedon-eachface thereof and near the periphery with rings '35havingaseriesof apertures to receive the pins 36 passing :through thebearings-'24 of the vanes23. The pins fst may be slightly hammeredorswagedover the rings :35 so'that the same are held .in assembly with thedisk 22 and the vanes 23. 'Thustheflisk 22, the rings 35, the vanes .23and shaft I9 forma single 'andunitary assembly.

In operation it is desired to provide a mechanical means for initiallydisplacing each vane from its collapsed position, thereby permitting theingress of compressed fluid'betweenthevane and its seati32, which causesthe pressure of thefiuid to be applied against theifiat "face of thevane and maintain its free edge 29 in'engagement with the stator.For'this purpose the present invention provides a spring pressed ejectorpin 40 which presses against the flat 'or inner face of .the vane 23when it1is 'in its collapsed position andserves to'move it into'itsslightlyopen-contuition as shownat 31.

The ejector pin 40 is the operating element in a small structuralassembly which includes a cup shaped element 4! having an aperturedhottom 42 and providedwith an 'enlarged and exteriorly threaded outerend-43. Thepin 10 is disposed within :the cup M :andits lower .end '44passes through the opening .in the'bottom .112. 'The pin 40 is alsoprovidedwithan enlargement 45 "at its other end whichsomewhat'approximates the inner diameter .of'thecun il. A helical springA6 is disposed-between the :collar iii-and the bottom-42. The portionof'the cup'M is preferably providedxwith'an inwardly directed projectionM which serves as a stop for the outward movement of the ejector A l..This unitary assembly is housed in :a well 48 formed :in the 5,588.17:32 near the heel of the vane. The outer end ;of the well 48 isinteriorly threaded so as to 'receive the exterior threads of theportion'ds. The ejector assembly is preferably so mounted within thewell 48 that the end face of thecup 4'! is substantially flush with theseat '32 and consequently the vane impellers 23 may be seated flushagainst the seats 32 as shown in the positions 33 and -34, and "thespring 45 is thus compressed, so that the pin may act upon the vane tomove it away from the seat 32 and keep it in this position until itpasses the fluid pressure inlet. The fluid pressure will then take upwhere the ejector pin left off and will maintain the vane in sealingengagement with the stator and by its pressure against the vane, willrotate the rotor.

The stator provides a pair of journal boxes for the ends of the shaftIll. The journal boxes are eccentric of the periphery of the circularstator. The interior of the stator which receives the rotoris ofgreaterdiameter than the rotor disk 22. When the :rotor and stator areassembled a crescent shaped space 49 is made available, within which thevanes 23 of the rotor operate to move from the collapsed position shownat :34 .to *a fully extended position and then to the :collapsedposition 33. This crescent shaped spacehas an inlet Hi, preferably inthe thin end of one of its horns and an outlet [5 in a regionimmediately past the maximum width of the crescent. The maximum width ofthe cres- 'centis preferably such that the vanes 23 when fully extendedoccupya position short of radial.

In operation the vanes withzthe :extending portions of the :gasket "formwhat may (be :termed movable :diaphragms that effect .a seal :againstthe adj acent faces of "the :stator. Thus the space :between each pairof vanes, smiled :at .each end .by the gaskets 28, formsa chamber whichexpands toamaximumduring 'one half'a revolution and contracts-duringtheesecond half .The stator embodies: an essential feature "of the:35:present:invention'inrthatit containszmeans'which .cooperate with:the rotor :and particularly with the impeller vanes s oias :to minimizethe friction, heat *and'othercpower losses. :Broadly stated-the statorof the present invention :comprisesan 403111111131 surface elementsupported :by antifriction ball bearings, and ithis element is free tomove with the vanes :23. This phase of the invention will be more 'fullyunderstood from the following detailed description of the structure andorganization of the-stator.

The stator 20*comprises-a pairof disks 5G and 2 5i, and a cylindricalspacer 52 disposed between the peripheral porticns of the plates 58 andSt. The specifiushape-and construction of the an- 0 nularelement 52ismore clearly'shown-inrFigure --9 :of the drawings. .It will Joe-seenthat this e1cment-has a seriesofitransverse external ribs 53 eachprovided with a longitudinal passage therethrough which receive thebolts 54 which-secure :theplates and 5l and thespacer '52 together andserve :to hold vthe entire engine in assembled relation.

The plate 5iis shown'as being provided with a series of radialreinforcing ribs 55 and if desired the plate or -'disk .50 .may also,rbe provided with such reinforcing ribs. The disks or plates 58 JandIElarezcircular and have=a.-diameter substantially'greater-than.thediameterof .the rotor 2i. l/Vhile the rotor .disk22 ;is providedwith a shaftwhich .is concentric with its periphery, the journal boxes 56 of thestator are eccentric with reference to .the peripheryof the stator. Thejournal boxes 56 have bronzebushings 51 and packing glands 58 to prevent.the escape of fluid lengthwise of the rotor shaft 19. The journal boxreceiving the'stub end of the shaft i9 is provided with a closure cap"'59. The cap 59 also has an integral sleeve portion 60 which isexteriorly threaded and'engages the interior threads 3: in the journalbox. The portion 60 also serves as a follow up for the packing gland 58and generally serves to provide an effective seal at this end of theshaft. At the opposite end of the shaft 19, namely, the end that extendsoutwardly and serves to transmit the power, the closure cap 6| threadson to the exterior of the journal box 56 and the follower 62 is disposedwithin the closure cap 6|. The follower 62 serves to press against thepacking gland 58 and to provide an effective seal at this end of theassembly. The closure cap 59 is provided with a central passage 65 whichregisters with an axial passage E36 in the shaft l9. The passage 66 alsohas radial passages 61, 68 and 69. Lubricating oil under pressuresupplied to the passage 65 therefore enters the passage 65 and is fedthrough the radial passages 61 and 69 to the bearings 51. The radialpassages 68 are in registry with radial passages Win the rotor disk 22which supply lubrication to the bearings 24 of the impeller vanes 23.

The inner faces of the stator disks 5t and 5! are provided with annularrecesses H concentric with the journal boxes 5%, these recesses beingdesigned to receive the annular rings 35 mounted on the peripheralportions of the rotor disk 22. The inner faces of the stator disks arealso provided with annular recesses 12 which receive packing glands l3interposed between the disks and the annular sealing element 52. Theplates or disks 50, El are each provided with a shoulder enlargement atthe inner end of the journal boxes 56, these serving to receivecorrespondingly shaped bosses it in the center of each face of the rotordisk 22 and thereby assisting in the proper centering of the units whenthe same are assembled.

In apparatus of the type to which the present invention is directed ithas been common practice to cause the free ends of the impeller vanes tooperate against the fixed annular surface of the stator. Such operationhas caused excessive friction, excessive temperature rise, and excessivewear of the cooperating parts, with a consequent lowering of theefficiency of the entire apparatus. One of the essential features of thepresent invention resides in providing a structure in which thesedifiiculties are minimized. In the present invention, therefore,antifriction means are interposed between the impeller vanes and thefixed annulus 52. Such antifriction means provide an effective seal bycontact with thetoe 38 of the vanes and with the portion 2% of theleather gasket. The antifriction means of the present invention,however, is free to rotate and is rotated by the force exerted by thepressure of the vane 23 against its face.

The antifriction means is part of the stator assembly. Its essentialelement is the revoluble annulus indicated by the reference character88. Its inner diameter is such that it exceeds the diameter of the rotordisk 22 by an amount approximately the same as the length of theimpeller vane 23 extending beyond the periphery of the rotor disk 22.This arrangement is preferably such as to prevent the impeller vanesfrom ever assuming the radial position. Thus the greatest extensionoutward of the impeller vanes 23 is best illustrated in Fig. 3 by thetwo lowermost vanes. The inner face of the revoluble annulus 80 ispreferably polished or machined so as to reduce the friction and itsouter face is provided with a pair of annular grooves 8| receiving ballbearings 82.

In order to provide for a ready and facile adjustment against possiblewear of the revoluble ring or its grooves 8i a pair of rings 83 and 84are interposed between the revoluble ring 80 and the sealing ring 52.Each of the rings 83 and 84 is provided on its interior face with anannular groove 85, 86 respectively which cooperate with the grooves 81to receive the ball bearings 82. Preferably the grooves 85 and 86 aresomewhat deeper than the grooves 8i. Annular packing glands 87 and 88are disposed in the recesses 89 provided for this purpose in the facesof the stator disks 50 and 5|. The revolu-ble ring iii bears against theone face of the packing glands 8'! and 88 while the rings 83 and 86 bearagainst the other face of the packing glands 8i and 8B.

The annular element '52 is provided with a circumferential rib 90 whichis shown in Fig. 9. The

rib 90 has interiorly threaded radial passages 9! which receive screws92. The screws 32 are tapered at their free ends and extend intoregistering recesses in the adjacent faces of the rings 83, 84. When theball races have worn the screws 92 are turned slightly inwardly and thetapered ends will operate to separate the rings 83, 84. This willproduce a more positive engagement between the rings and the ballbearings for the ball bearings will then be engaged more firmly by oneor the other side of the races. The passages 93 provide for theintroduction of lubricating oil to the ball bearing.

In operation the fluid pressure is exerted against the fiat faces 28 ofthe vanes 23 and the rotor is rotated in the clockwise direction in Fig.3. The space between each pair of vanes may be said to constitute anexpansible chamber, for as the rotor rotates this space is enlarged byreason of the eccentric arrangement of the rotor with reference to thestator. Thus the pressure within each chamber is continuously reduceduntil the outlet i5 is reached when the fluid, compressed air or steam,exhausts. The pressure causes the vane to press against the inside faceof the annulus ii The annulus 89 will thus rotate in the same directionas the rotor. It should be noted that the linear speed of the toe of theextended vane as shown at the bottom of 3 is cfin dcrably in excess ofthe linear speed of the top of the rotor. Thus even when there is nodiiTerential speed at the bottom there will always be differential speedbetween the rotor and annulus 80 at the top of the rotor. It is in thehigh pressure zone, which is in the space between the inlet and outletand subtends an angle only somewhat greater than one quadrant, where thefriction losses occur. In the remaining three quadrants the vanes exertno substantial pressure against the stator. It is, therefore, desirableto minimize relative motion between the vanes and annulus 80 in the highpressure zone and permit relative movement in the low pressure zone. Itwill now be understood that the present construction provides for suchdistribution of relative motion with the consequence that frictionlosses are minimized or greatly reduced.

It is not necessary that the linear movement of the annulus 8i! shouldapproximate the toe of the Vane when extended. For the several vanesoperating in the high pressure zone are variously extended and theirtoes operate at different linear speeds. The linear speed of the annulustil will thus vary with the operating pressures, the rate of rotation ofthe rotor and the number of vanes in the high pressure zone. In allcases however the present invention provides for minimizing the relativemotion between the vanes and the am i7 nulus 88 in the-zone where thegreatest friction lossescommonly occur.

Even in the low pressurezones the relative motion between the annulus 8Band the rotor is much smaller than it would have been if the ballbearing mounted annulus 8b were not employed. Thus the friction lossesin the low pressure zone are also greatly reduced.

In order to control the operation of the motor the inlet id is providedwith-a valve for controlling the amount of fiuid that enters the space49. For this purpose the disk i is provided with an integral upstandingsleeve e4 which surrounds the inlet M. The sleeve 96 has a-lateralopening-95. A valve cup S6 having an openin 9! encircles sleeve as andcloses its upper end and is provided with a stem 98 for rotating it toadjust the size of the overlapping portion of the openings'95, 97 tocontrol the flow of operating fluid or to close off the valve and stopthe motor. The cap :99 is bolted to plate 5! by screws N36. The caphas-the nipple ill! for connection to. the source of fluid and anopening 552 which registers with opening Fig. 10 illustrates the presentinvention embodied in a two stage engine or motor. Briefly in this twostage motor the fluid enters the first stage and while still undersubstantial compression it exhausts into the second stage and thence toatmosphere or to a condenser, if the source of power is steam.

In Fig. .10 the "elements or parts which are identical with thecorresponding parts in the single stage motor shown in Figs. 1 to 9 areindicated by the same reference character.

Thus the two stage motor has two rotors 22 and 228 which are separatedby a-spacer 22!, and the shaft [9 passes through both rotors and isspliced to both rotors. The inlet M for the first stage is indicated bydotted lines in the stator plate 5%. At about a quadrant distant theoutlet from stage i is in the spacer 22! as shown in dotted lines at222. The spacer 22| has an arouate interior passage 223 running parallelto its side walls, which opens at 224 into the space 496 of the secondstage motor. Thus the compressed fiuid first does work in the firststage and then enters the second stage at this reduced pressure. Becausethe pressure is reduced the vanes23ll of the second stage are wider sothat the reduced pressure multiplied by the greater area of the vanes236 will result in the production of work'by each vane 23! whichapproximates the work done by vane 23 in the first stage.

The stator disk 55 has the exhaust port 1 5. The

embodiment shown in Fig. 10 may be employed with compressed air but itis provided with a condenser chamber 23! so that if steam is'employed,it may be condensed before it is exhaustedto the atmosphere. The chamber23! is formed by the cylindrical side wall 232 which has an annularflange 233, which is boltedagainst the stator disk 58 by the bolts 5 Theend wall of the chamber 23! is in the form of an annularly corrugateddisk 23 2 which may be integral with the side wall 232. The end wall 23%has a central opening and its edge is preferably clamped between the cap59 and the journal box 56.

It will be understood, of course, that various changes and modificationsmay be made in the construction shown in the drawings and ashereinbefore described without departing from the .general principles orreal spirit of the present invention, and it is intended to claim thesame broadly as well asspecifically as indicated in the appended claims.

-I claim:

1. A fluid motor having in combination a pair of spaced disks, each diskhaving aneccentric journal box, an annular member disposed between theperipheral portions of said disks and assembled therewith to form afixed stator, ,a freely rotatable annulus disposed within said statorand spaced from said annular member, said annulus having a pair ofparallel ball bearing race grooves on its outer face, a pair oflaterally spaced rings disposed between said annulus and said annularmember, each having a ball bearing race groove on its inner face inapproximate registry with one of said ball bearing races on saidannulus, two courses of ball bearings interposed between said rings andsaid annulus, means for ad justing the rings to compensate for wear,and'a rotor fixed on said shaft, said rotor comprising a circular plateand a plurality of impeller vanes pivoted on the periphery of saidplate, the toe portions of said vanes operating against the annulus andcausingits rotation.

2. A fluid motor having in combinations. pair of spaced disks, each diskhaving an eccentric journal box, an annular member disposed between theperipheral portions of said disks and assembled therewith to form 'afixed stator, a freely rotatable annulus disposed within said stator andspaced from said annular member, said annulus having a pair of parallelball bearing race grooves on its outer face, a pair of laterally spacedrings disposed between said annulus and said;annular member, each havinga ball bearing race groove on its inner face in approximate registrywith one of said ball bearing races on said ,annulus, two courses ofball-bearings interposed'between said rings and said annulus, a seriesof radial screws carried by said annular member, the ends of said screwsbeing tapered and disposed between said rings, said screws thus servingas means for adjusting the rings to compensate for wear, a rotor fixedon said shaft, said rotor comprising a circular plateand a pluralit ofimpeller vanes pivoted on the periphery of said plate, the toe portionsof said vanes operating against the annulus and causing its rotation,and a flexible gasket carried by each vane for sealing engagement withthe inner face of saidannulus.

3. A fluid motor having in combination a pair of spaced disks, each diskhaving an eccentric journal box, an annular member disposed between theperipheral portions of said disks and assembled therewith to form afixed stator, a freely rotatable annulus disposed within said stator andspaced from said annular member, said annulus having a pair of parallelball bearing race grooves on its outer face, a pair of laterally spacedrings disposed between said annulus and said annular member, each havinga ball bearing race groove onits inner face in approximate registry withone of said ball bearing races on said annulus, two courses of ballbearings interposed between said rings and said annulus, a series ofradial screws carried by said annular member, the ends of said screwsbeing tapered and disposed between said rings, said screws thus servingas means for adjusting the rings to compensate for wear and a rotorfixed on said shaft, said rotor comprising a circular plate, a pair ofannular bands disposed on the lateral faces of said plate, a pluralityof radial impeller vanes carried by .saldicplates, the toe Portions ofsaid vanes operating against the annulus and causing it 9 rotation, eachVane having a flexible gasket for Sealing engagement with the inner faceof said annulus, said disks having an inlet opening and an outletopening.

HENRY J. SHARP.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 8,686 Huse Jan. 27, 1852 800,633Dengler Oct. 3, 1905 Number Number

